Selective one-way drive



srovse C S. C. WINGER Filed June 20, 1949 SELECTIVE ONE-WAY DRIVE Aug. 18, 1953 INVENTOR. WNGER,

, the blade of a screw driver).

Patented Aug. 18, 1953 SELECTIVE ONE-WAY DRIVE Stover C. Winger, Los Angeles, Calif., assignor of fifteen per cent to John Flam, Beverly Hills,

Calif.

Application June 20, 1949, Serial No. 100,239

5 Claims.

This invention relates to tools, and particularly to screw drivers.

that the blade may be kept in contact with the screw slot continuously; the handle is merely given alternate reverse and forward angular movement.

It is one of the objects of this invention to provide a simplified screw driver, operating in this fashion.

It is another object of this invention to provide a simple and effective clutch between a driving member (as for example the handle of a screw driver) and a driven member (as for example In it broadest aspects, such a clutch incorporating the invention is useful in many types of mechanism where rtary power is to be transmitted selectively or 01)- tionally in either direction of movement.

It is still another object of the invention to provide a clutch mechanism that may be op- V tionally adjusted in a simple manner to drive in either direction.

It is still another object of this invention to simplify a structure of thi character, and to facilitate assembly of the operating parts.

This invention possesses many other advantages, and has other objects which may be made more clearly apparent from a consideration of a form in which it may be embodied. This form is shown in the drawings accompanying and forming part of the present specification. It will now along planes corresponding to lines 2-2, 4-4,

'I-I and 8-8 of Fig. 1;

Fig. 3 is a fragmentary view, similar to Fig. 1, illustrating an alternative position of the drive mechanism;

Fig. is a view similar to Fig. 4 illustrating the manner in which a drive is effected between the handle and the hank;

Fig. 6 is a sectional view, taken along a plane corresponding to line 66 of Fig. 3.

The screw driver includes a handle I, which may be made of wood, plastic, or other suitable material, and a shank or shaft 2. The shank 2 terminates in a flattened blade 3 that may be inserted into a slot in the head of the screw to be driven.

A clutch mechanism is interposed between the handle I and the shank 2 in order to make it possible to drive the shank 2 in either direction upon reciprocatory angular motion of the handle I. One element of this clutch is provided by an annular member 4 in the form of a metallic tube. The tube 4 is rigidly fastened into the cylindrical recess 6 formed in one end of the handle I. It projects considerably below the handle I to form the internal cylindrical clutching surface 5. The upper end of the shank 2 is free to rotate with respect to the handle I. For this purpose it is inserted within the hollow cylindrical socket member I (see, also, Fig. 8). Externally of cylindrical member I a plurality of radial webs or vanes 8 are integrally formed. The ends of the radial vanes are pressed into the annular member 4. At the lower end of the member I there is a flange 9 which covers the annular space between the socket I and the annular member 4.

The shank 2 is shown in this instance as formed of hexagonal stock. Its cross section thus presents parallel plane faces. It is removably retained within the socket member I by friction, as by providing an expanding spring ring II] in a groove formed near the upper end of the shank 2. Furthermore, as clearly shown in Fig. 8, the diagonal of the hexagonally shaped cross section of the shank 2 corresponds substantially with the internal diameter of the member I, so that there is no restraint against relative angular movement between the shank 2 and the handle I.

In order to drive the shank 2 by the aid of the handle I, use is made of a pair of clutch segments II and I2, cooperating with annular member 4. These segments may have flattened tops, as indicated at I3, and have cylindrical surfaces adapted frictionally to engage the internal surface 5. As shown most clearly in Fig. 4, the opposite parallel faces of the shank 2 are received between the plane surfaces I 4 and I5 of the segments II and I2. Furthermore, at this place the corners of the hexagon are slightly rounded. There is only a small amount of clearance (of about one or two one-thousandths of an inch) between the parallel faces of the shank 2 531d the contiguous faces of the segments II and The segments II and I2 may be expanded, or urged apart, into frictional engagement with the internal surface by rotation of the handle in either direction. Thus, for example, the rotation of the handle in a counterclockwise direction, as viewed in Fig. 5, causes opposite corners of the hexagonal shank 2 to engage the plane surfaces of the segments II and I2 and to wedge them apart into firm frictional engagement with the internal surfaces 5.

Accordingly, as thus far described, a slight angular movement of the handle I and its attached annular member 4 serves to cause Wedging of the segments II and I2 into driving relation with the shank 2, and the shank 2 is correspondin ly rotated. This occurs for either direction of rotation of the handle I.

In order to confine the segments II and I2 against substantial axial movement, use is made of a bushing member I6. This bushing member I6 has a flange I1 telescoping into the annular member 4, and retained therein, as by friction. The segments I I and I2 are confined between the lower surface of flange 8 and the upper surface of flange II.

In order to make it possible to reverse the angular motion of the handle I without rotating the shank 2, means are provided for restraining relative angular movement between the shank 2 and the segments II and I2 during reverse rotation. In Fig. 6, a restraining means is shown as interposed between the segments II and I2 to prevent angular movement of the segments II and I2 in a clockwise direction. Thus, a pair of abutments I8 and I9 are shown, which cooperate with the short projections 28 and 2| carried by the segments II and I2. These abutments I8 and I9 may be considered, for the present as fixed. They are in such angular relationship with respect to the segments I I and I2 that the plane segments II and I2 by friction into engagement with opposite corners of the shank 2, and coupling is therefore effected between the handle I and the shank 2. The handle I can then be rotated in a counter-clockwise direction for rotating the shank 2. The handle, however, is free to rotate a in a clockwise direction.

In order to make it possible to reverse the direction of the drive, the abutments I8 and 59 are carried on a slide movable along shank 2 which slide carries another set of abutments axially spaced from the abutments I8 and I9.

Thus, splined to the shank 2 is a slide 22. This slide, as shown most clearly in Figs. 1, 3 and '7, is guided for movement in the bushing member I6. It is provided with a hexagonal aperture permitting it to be adjusted axially with respect to the shank 2, while relative rotation between the slide and the shank is prevented.

Theslide 22 carries diametrically opposite projections 23 and 24. These projections are joined over the lower end of the slide 22.

4 integrally to the slide 22 by the connecting members 25 and 26. As shown most clearly in Figs. 4, 5 and 6, the projections 23 and 24 enter between the segments II and I2. The projections 23 and 24 extend generally in an axial direction, and carry at opposite ends thereof the pairs of sets of abutments I8 and I9 (appearing at the lower end of the projections 23), and the abutments 21 and 28 (extending from the upper end -of the projections 23 and 24).

The abutments I9 and 21, as shown most clearly in Figs. 1 and 2, face in opposite directions from the projection forming a substantially Z-shaped member. Similarly, the abutments I8 and 28 extend in opposite direction of the projections 24.

The slide 22 is shown in adjusted position in Fig. 1, in which neither of the sets of abutments 18I9 or 27-28 is effective to restrain relative angular movement of the segments II and I2. Accordingly, the screw driver may be operated as an ordinary screw driver, the handle I being in continual driving relation with the shank 2 for either direction of rotation (see Fig. 4).

In Fig. 3, the slide 22 has been moved to its extreme upper position. This upward movement is limited by the contact of the abutments 21 and 28 with the lower surface of flange 9. In this position, the abutments I8 and I9 contact the projections 2t and 2| of the segments 4 I and I2. Accordingly, the handle I is coupled to the shank 2 only during counter-clockwise rotation of handle I (seeFig. 6).

Now, assume that the slide 22 is moved to its extreme lowermost position, as indicated by the dotted lines 29 in Fig. 3. Under such circumstances, the abutments 21 and 28 cooperate with the projections 38 and SI of the segments II and I2. Obviously, this would cause coupling of the handle I to the shank 2 only for clockwise direction of rotation.

The amount of angular rotation necessary to cause expansion of the segments II and I2 is quite small. This small relative rotation is secured by providing relatively close limits of clearances between the annular member 4, the segments II and I2, and the shank 2.

The slide 22 has a cap 32 threaded exteriorly This cap serves to confine a contracting spring ring 33 in a recess formed in the lower end of the slide 22. This spring ring is intended to engage an interrupted groove 34 provided on the shank .2. When the ring 33 is in the groove 34 (Fig. 1), the screw driver handle I is continuously coupled to the shank 2. The slight resistance 'to movement of the slide 22, provided by the spring ring 33, is .sufiicient to indicate to theuser when this particular setting is effected. No such indication is required for the other two positions of the slide. The slide 22 is limited, as heretofore stated, in its upward movement by contact of a the abutments 21 and 28 with the lower surface and taken apart.

1 annular member 4, since these two parts are held together frictionally. The segments I-1 and 12 are then readily removable at the same time that the shank 2 is pulled out of the cylindrical member 1. The reverse process of assembling the parts is apparent;

The inventor claims:

1. In a clutch mechanism: a shaft having angularly spaced flat surfaces; means providing a recess into whichthe shaft extends, said recess forming an internal cylindrical friction surface coaxial with the axis of the shaft; a plurality of segments having cooperating friction surfaces and having plane surfaces cooperating respectively with the flat surfaces of the shaft, the clearance between the plane and flat surfaces being such that relative angular rotation in either direction between the shaft and the segments produces a wedging of the friction surfaces against the cylindrical surface; and means slidable along the shaft and non-rotary with respect thereto, for selectively-restraining relative an ular movement between the shank and each of the segments in either of the two directions of relative movement, including a pair of sets of abutments, each set providing a simultaneous restraint for each segment.

2. In a clutch mechanism: a shaft having angularly spaced flat surfaces; means providing a recess in to which the shaft extends, said recess forming an internal cylindrical friction surface coaxial with the axis of the shaft; a plurality of segments having cooperating friction surfaces and having plane surfaces cooperating respectively with the fiat surfaces of the shaft, the clearance between the plane and fiat surfaces being such that relative angular rotation in either direction between the shaft and the segments produces a wedging of the friction surfaces against the cylindrical surface; and means slidable along the shaft, and non-rotary with respect thereto, for optionally preventing engagement of the flat and plane surface, including a pair of sets of abutments, each set providing a simultaneous restraint for each segment.

3. In a clutch mechanism: a shaft having angularly spaced flat surfaces; means providing a recess into which the shaft extends, said recess forming an internal cylindrical friction surface coaxial with the axis of the shaft; a plurality of segments having cooperating friction surfaces and having plane surfaces cooperating respectively with the flat surfaces of the shaft, the clearance between the plane and flat surfaces being such that relative angular rotation in either direction between the shaft and the segments produces a wedging of the friction surfaces against the cylindrical surface; and means slidable along the shaft and non-rotary with respect thereto, for selectively restraining relative angular movement between the shank and each of the segments in either of the two directions of relative movement, comprising two sets of axially spaced abutments for selectively preventing relative rotation in either direction, each set providing a simultaneous restraint for each segment.

4. In a clutch mechanism: a shaft having angularly spaced flat surfaces; means providing a recess into which the shaft extends, said recess forming an internal cylindrical friction surface coaxial with the axis of the shaft; a plurality of segments having cooperating friction surfaces and having plane surfaces cooperating respectively with the flat surfaces of the shaft, the clearance between the plane and flat surfaces being such that relative angular rotation in either direction between the shaft and the segments produces a wedging of the friction surfaces against the cylindrical surface; and means slidable along the shaft, and non-rotary with respect thereto, for selectively restraining relative angular movement between the shank and each of the segments in either of the two directions of relative movement, comprising two sets of axially spaced abutments for selectively preventing relative rotation in either direction, each set providing a simultaneous restraint for each segment, there being sufficient axial spacing between the 'two sets to permit intermediate positioning of the slidable member to cause wedging for both directions of relative rotation.

5. In a clutch mechanism: a shaft having angularly spaced flat surfaces; means providing a recess into which the shaft extends, said recess forming an internal cylindrical friction surface coaxial with the axis of the shaft; a plurality of segments having cooperating friction surfaces and having plane surfaces cooperating respectively with the flat surfaces of the shaft, the clearance between the plane and flat surfaces being such that relative angular rotation in either direction between the shaft and the segments produces a wedging of the friction surfaces against the cylindrical surface; and means slidable along the shaft, and non-rotary with respect thereto, for selectively restraining relative angular movement between the shank and each of the segments in either of the tWo directions of relative movement, comprising two sets of axially spaced abutments; one set restraining relative angular. movement between the segments and the shaft in one direction, and the other set restraining relative angular movement between the segments and the shaft in the other direction, each set providing a simultaneous restraint for each segment, said slidable member being positionable to cause either or neither of the sets to be active.

STOVER C. WINGER.

References Cited in the file of this patent UNITED STATES PATENTS Number Name Date 333,143 McDonald Dec. 29, 1885 849,487 Morse Apr. 9, 1907 1,158,765 Aiken Nov. 2, 1915 2,299,739 Colucci Oct. 27, 1942 2,463,220 Van Hoose Mar. 1, 1949 2,463,221 Van Hoose Mar. 1, 1949 

